DE2048975A1 - Integrated drive and generator connection removed from 2044441 - Google Patents

Description

P.1573

Sundstrand Corporation xtockford, Illinois, V.cJt.A.

Integrated drive and generator connection

χάβ invention relates to an integrated constant 'iesciiV / inuigiceitsantrieb and G-enerator for use Suitable for creating electrical power for aircraft are.

In the past, constant timing drives mounted on aircraft engines have been created for the purpose of maintaining a constant output speed with changes in engine speed, e.g. 9OOÜ rpm .. Such a drive is in the üa-j ^ atent ür. 2,365,981. Driven by these drives are enerators in the range of 30 - 150 Kilovoj.tampere, welcae beispiexsv / eise electricity of 400 ierioaen ^ um operation of i'lu ^ vehicle equipment and accessories.

ffen.

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These two units i.e. the constant speed drive unit and the generator unit has usually been completely independent units in the past different manufacturers have been designed and only attached to each other for the purpose of assembly and drive.

The constant speed drive units generally include a gear differential driven by the motor, effective displacement hydraulic pumps and motor units to control the speed ratio of the differential gear and regulator-operated control circuits to change the displacement of the hydraulic units in order to achieve a constant speed output, as well as mud, lubrication and charge fluid circuits for these components. The constant speed drive housings are sealed housings, separate from the Generator housing been.

The generators that usually run with these constant speed drives have also included independent sealed housings with stator and rotor, which are fully supported and mounted in it. An independent lubricant circuit for bearings, seals and keyways have been provided when necessary. The rotor and stator are conventionally air cooled.

Ee is for constant speed drives and generators have been found desirable, the same by providing units of smaller size, light weight, and taller Improve reliability. The constant speed drives themselves have a remarkably higher reliability, i.e. the average time between failures is far longer on the constant speed drives than on the

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Generators themselves and this divergence stimulates the search for the design of the present integration of the constant Speed drive and generator leads in a substantially common housing.

In particular, the invention creates an integrated drive and generator connection which contains a generator a stationary stator and an itotor that works with essentially constant speed can be driven, a constant Speed drive to drive the Hotor which includes an input shaft member driven by a main drive can be driven, an output shaft member connected to drive the rotor, a first hydraulic unit, which is drivingly connected to one of the shaft members, a second hydraulic unit, conduit means, which are hydraulically connected to the first and second hydraulic units, a control device to the Displacement of one of the hydraulic units change to maintain a substantially constant Hotorspeed to get, with a differential gear between the Input and output shaft members includes a timing gear, to vary the speed of the output shaft member with respect to the input shaft member, the second hydraulic unit is drivingly connected to the control gear, further housing means for the generator, the called differential and hydraulic units, means for supplying control fluid to the control means supply, means to supply hydraulic fluid to the generator and a common sump in the Housing device for both of the aforementioned fluids.

There are several advantages of the invention over the prior constant speed drive and separate ones Generator units. First and foremost is the sealed

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or sealed wall between the constant speed drive and the generator has been turned off, as well as the need for rotating contact type seals at the mating ends of the generator and the constant speed drives as they are currently in use are. An additional advantage of the generator is that a common environment is provided with the drive components which is more beneficial than being open to the atmosphere, as was the case in earlier Pall air-cooled generators. The groove life in the generator is also increased due to continued lubrication by fluid from the single charge pump located in the drive housing is. If desired, a single set of pumps can be used for flushing, charging, cooling and lubrication functions for both Drive and generator, may be provided which are more conveniently housed in the constant speed drive part of the housing from which arises in space and weight, since they can be easily driven from this point and their number is reduced.

Another advantage of the invention is that one of the differential elements is in line and directly with the generator rotor connected and rotating at the same speed, eliminating the need for interlocking Gears between the differential and the generator are turned off.

The whole differential is with both the encoder axis as aligned with the input shaft so that an additional gear is switched off between the input shaft and the differential is.

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In this way , two hydraulic drives are controlled in parallel by a single glider , which reduces the maximum diameter of the integrated constant speed drive and the differential.

Furthermore, it is possible for generators to operate continuously with as much as 150.6 of their estimated load without damage, whereas in conventional air-cooled generators such overloads can only be allowed for a few minutes.

In the drawings showing, for example, embodiments of the invention are:

1 is a schematic view of an embodiment of the invention, FIG. 2 is a longitudinal cross-section of an integrated drive and

Generators in general, similar to that in Pig. 1 shown, Pig. Figure 3 is a cross-sectional view taken generally along line 5-3 in Figure 2 with the charge pump and scavenge pump mounting surfaces

and channels are shown tfig. 4 is a cross-sectional view taken generally along line 4-4 in FIG. 2 with the charge pump and wash pump in position along with

the controller are shown,
Figure 5 is a partial section taken generally along line 5-5

in Fig. 4 showing the charge pump filter; Fig. 6 is a cross section taken generally along line 6-6 in Fig. 2;

showing several of the charge pump passages, X- ¹ Ig. Figure 7 is a partial section, generally along line 7-7

in Fig. 4,
jj'ig. 8 a partial section, generally along line 8-8 in i ⁽¹ ife,. 6,

9 is a partial section taken generally along line 9-9 in FIGS. 4, showing the inlet passage for the stator cooling air flow passage,

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Figure 10 is a partial section taken generally along line 10-10

in Fig. 4, with the return passage for the otator-

cooling fluid is shown, Figure 11 is a partial section taken generally along line 11-11

in Pig. 4, with the stator cooling fluid flow

corridors shown bind, Figure 12 is a partial section taken generally along lines 12-12

in Pig. 11

Figure 13 is a partial section taken generally along lines 13-13 in Pig. 4,

Fig. 14 is a partial section) showing the generator housing

eumpf shows Figure 15 is a partial section taken generally along lines 15-15

in Pig. 6, showing the inlet re-reservoir vortex chamber

iet, Pig. 16 is a partial section, generally along lines 16-16

in Pig. 4, with the charge pump raised, FIG. 17 a partial section of FIG. 4-AbeohnitteB, Pig. 18 a partial section generally along line 18-18

in Pig. 17, whereby the Tranemieeion displacement tax

controller shown iet,

Pig. 19 is a partial section generally along line 19-19 "in Pig. 17, the hydraulic displacement control

engine shown iet, Fig. 20 is a schematic representation of another embodiment

the invention, Fig. 21 is a hydraulic circuit diagram for the integrated

constant speed drive and generator that

are shown in Fig. 20, and FIG. 22 shows a longitudinal section of the drive part of FIG. 20

execution shown.

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in the drawings and in particular in that in Pig. 1, there is shown an integrated constant speed drive and generator 10 with its associated hydraulic circuit, some parts being enclosed in the housing for the unit and some parts not, as shown below. The integrated, constant speed drive 10 can be mounted on the motor gear housing of the associated plug-in motor, the input line 12 being set in rotation by the motor through the gear housing. It will be understood that the shaft 12 η can vary in speed with the motor and so can vary in speed from zero to 9000 rpm during normal use with the proper plug-in tool design and gear box shape. The integrated drive train 10, however, is actually designed to provide a constant generator speed which provides a constant output shaft speed, e.g. 2000 rpm for input shaft speeds of shaft 12 on between e.g. to be included in normal engine speed ranges.

he integrated drive and generator 10 is shown in general'n a drive housing 14 with a ydraulischen drive 15 contains therein, as well as a generator housing 17 with a generator 18 located therein, the it is connected to the drive housing 14 with a differential 20 which is partially mounted in each of the housings 14 and 17 is.

de üingangswelle 12 is with the differential gear carrier 2 coaxially and drivingly connected, which rotatably interlocking tickle 24 and 25 carries. The gear carrier FIG. 2 also has a ring 28 mounted for rotation therewith, unless it has a gear thereon which engages with gear 30. FIG m engagement connected to a variable hydraulic displacement axial piston unit 34.

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The hydraulic unit 34 is hydraulic through suitable lines (not shown in Fig. 1) with a fixed one hydraulic displacement unit 36 connected, which also belongs to the axial piston type. The hydraulic unit 36 is driven by the gear 38 with a stepped sleeve ring gear 40 connected, which, as at 41, has internal teeth that mesh with the pinion 24.

The differential 20 also includes another sleeve type Ring gear 48 with internal teeth 491 located thereon, which mesh with the pinion 25 and thereby rotate are driven. The components previously described generally determine what is known in the art as a Output / cBfferential is called. With the carrier 22, the The hydraulic drive 15 serves as the input and the sleeve ring gear 48 which functions as the output suitably variable to control the speed of the control sleeve ring gear 40 to a constant To provide output speed of the output ring gear 48.

The output ring gear 48 is through a suitable overrunning clutch 52 connected to the drive generator rotor 54. The generator rotor 54 is at its left end in the housing 17 supported by bearings 56 and at its right end by output sleeve bearings 57 and 58 by bearings 72 between the Sleeve 48 and a central shaft 73. Me central shaft 73 rotates with the shaft 54 as a result of the connecting function of the Rotor sleeve 70, which in a suitable manner on both './eilen 54 and shaft 73 is attached.

That is, the output sleeve is supported in the housing part 76, the shaft 73 is supported in the output sleeve 48

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and rotor shaft 54 is fixed to rotate with shaft 73 with sleeve 70 with the alignment therebetween is held upright.

In operation, the controller 78, responsive to the speed of the exit sheath 48, provides control fluid through the Passage 80 to a control piston 82, which varies the displacement of the hydraulic unit 34 to the speed To control the ratio between the carrier 22 and the output 48 in order to maintain a constant speed of the rotor shaft 54 as the input speed of shaft 12 varies, so a constant frequency signal of Generator 18 is generated

The hydraulic system of the drive and generator 10, which is described in Pig. 1 is shown in purely schematic ϊοπη and it will be understood that all of the components and passageways shown are in fact within housings 14 and 14 with the exception of the purge filter 84 and the purge fluid cooler 85 »

The purpose of the lubrication system shown is to provide lubrication fluid to provide the drive and generator components, control fluid to the control circuit for change the transmission drive ratio and cooling fluid to be provided on the generator 18. For this purpose, a charge pump 88 is provided, which fluid by a Feed filter 89 to regulator 78 through passages 90,91. The cooling fluid is for the stator 92 of the generator 18 through passages 94, 95, 96 and 97 are provided. • Jai daa differential gear 20 as well as the generator grooves too bcnmieren, the Kotorwelle 54 is hollow and stands with the slack 94 in communication so that fluid is delivered through the rotor to the various gear elements in the differential as well as various of the

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Lubricate generator parts. Suitable ones can also be found in Pig. 1 means not shown may be provided to the rotor 98 with the Generator to cool. It is understandable that the cooling of the generator and stator through direct contact with the cooling hydraulic fluid takes place, which is delivered through the Durohgang 94 therethrough.

Fluid is fed to the hydraulic drive 15 by the Passage 98 is supplied and the excess capacity of charge pump 88 is passed through charge spill valve 100 Passage 101 to the inlet of a wash or sump pump 104 delivered. The wash pump draws fluid through passage 106 from a common sump 108, which with both housings 14 and 17 communicates so that the sump 108 collects fluid from the components in both housings. The cooling pump 104 delivers fluid through the passage 110, through the purge filter 84, and the cooler 85 through the passage 112 to a vortex chamber 114 in a Reservoir 115, which through a suitable septum in the housing 14, which separates it from the common sump 108.

The passage 118 conveys fluid from the reservoir container 115 to the inlet of charge pump 86.

The execution of the invention contained in the Pig. 2-19 is essentially the same as the eohematieche Representation in fig. 1 with the exception that the input shaft protrudes from the generator end of the integrated housing, rather than from the constant speed drive end same. In the longitudinal section view in Fig. 2 is a constant speed drive and generator combination 120, from which it can be seen that they are a generally

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ORIGINAL INSPECTED

includes a cylindrical energizer housing 122, the left end of which is open, and a generally cylindrical drive housing 124, the right end of which is open. J) The housing members 122 and 124 are fastened to one another by suitable fastening devices (not shown), an externally grooved input shaft 126 is inserted in bearings 128 and protrudes centrally from the generator housing. The input shaft 126, like the shaft 12 in FIG. 1, can be driven by one of the plug-in tool motors through a suitable gear housing. The input shaft drives a gear carrier 1JO of the gear differential through a sonic separating clutch 133. The quick disconnect clutch 133 can be actuated / grounded by a solenoid 136 which separates the motor from the drive 120.

The elongated pinion carrier 130 takes rotatably elongated ones itzel 134 and 135 to »which central, as at 138. Approved is to interlock. A stepped sleeved control ring gear 140 is provided so that it Rehbar is supported on the elongated gear carrier 130 by bearings 42 and 143. Teeth 144 are on that The real end of the sleeve gear 140 is molded in one piece amit and grip with pinions 134 on the left nd the gear teeth of the same. The left end of the similar gear carrier 130 is supported in the bearing 148, elclies is mounted in a bearing frame extension 149 which consists of a piece with a perforated support and an oheidewand 150, which is attached to the housing member 124 is formed.

in stepped output sleeve gear 146 is coaxial It is arranged in relation to the input shaft 126 as well as the sleeve gear 140 and is rotatable

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the gear carrier 130 through bearings 148 'as well as externally is supported by bearings 152 and 322 which act against generator shaft 158.

The whole differential is coaxially aligned with the input shaft and partly in the generator rotor shaft arranged or housed. The generator 160 includes a stator winding 161 which is fixed in the housing 122 is attached and a rotatable eotor 162 attached to the shaft 158 is attached. Ee are also suitable excitation windings P 164- provided which is a conventional part of alternators Bind The right end of the hollow rotor shaft 158 is rotatably mounted in the bearing 168 which is in a suitable approach in the end portion of the housing member 122 is inserted. The left end of the hollow rotor shaft 158 is in supported by the bearing 170, which is supported by the main septum part 150 is worn. In this way it can be seen that the right end of the differential works in the hollow Generator rotor shaft 158 is supported.

The generator or rotor 162 is by direct connection driven with the output sleeve gear 146, which k has internal teeth 168 that match the gear teeth on the right The end of 135 through the overrunning clutch 170 'comb the is arranged approximately centrally in the rotor shaft 158 with respect to the rotor 162.

In a similar way as in the construction according to Flg. 1, by appropriately controlling the speed of timing gear 140 with respect to the speed of input shaft 126 and carrier 130, the desired constant output speed of output ring gear 146 and rotor 162 can be achieved.

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For the purpose of controlling the speed of the sleeve ring gear es 140 is a variable displacement hydraulic drive 175 which includes a variable axial hydraulic displacement piston unit 177 as well a fixed hydraulic axial displacement unit 179. The swiveling cam 182 allows the displacement of the hydraulic drive 175 can be varied as desired to accommodate infinitive variations in the relative speeds of shafts 184 and 185 to achieve the driving force in this regard with the hydraulic units 177 and 179 are connected. Units 177 and 179 become ™ at times act as pumps and at other times as motors or igniters.

The hydraulic unit 177 is driven by the input shaft 126, through the gear carrier 130 and a hollow shaft 186 which is capped at the left end of the gear carrier 130 and rotatable at its left end by the bearing 186 'in the closed end of the Housing member 124 is supported. The shaft 186 has a gear 188 which is formed from one piece thereon and meshes with the gear 189 which is formed integrally with the hydraulic unit shaft 184. The hydraulic drive 175 ( is supported in the housing member 124 by bearings 188 ', which support the shaft 184 and by bearings 190, which supports the shaft 185. A gear wheel Iy2 is formed from one piece with the shaft 185, which with an external gear wheel 194 is in EiRx _ö reef of differential is formed of one piece with the Steuerhülsenz & hnrad HO, namely for the purpose of Oteu>; tion of the speed and of the Drehriciitung

control of direction and displacement, -:.; liockons 162 aua seixier neutrals or Ilullhub-

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The control gear HO can move in any direction of rotation Rotated at speeds sufficient to maintain a constant output shaft speed from the output sleeve gear 146 to maintain and accordingly the rotor 162, which is thereby set in rotation.

In FIG. 4, a charge pump 200 is provided to supply charge, control and lubrication fluids to the constant Speed drive as well as cooling and lubricating fluids to be supplied to the generator 160. The charge pump is

ψ supported on a mounting plate 201 (FIG. 3) which is formed in one piece with the housing member 124 and which extends generally transversely thereto in a plane adjacent to the diaphragm 150. The mounting plate 201 has an arcuate inlet channel 204 and an arcuate outlet channel 205. It will be understood that the charge pump 200 is removed from the view in FIG. Charge pump 200 supplies fluid under pressure through outlet passage 205 and tube 207 (FIG. 5) longitudinally rearward in housing 124 as seen in FIG is formed in the housing 124 and extends generally radially with respect thereto, as shown in FIG. 6. The charge filter 210 can be removed by removing the fitting 214. After passing through the charge filter 210, the charge fluid is delivered to an irregular passageway 216 which extends transversely near the end of the housing member 124 and is molded in one piece with the housing.

As can be seen in Fig. 18, a Hegler 218 is provided, which is mounted in the housing part 124 and extends longitudinally adjacent the closed end thereof. The bowler 218 includes a circumferential sleeve 219 and selectively directs fluid to a displacement control 222, shown in FIG. 19 is shown. The adjustment control unit 222 controls the

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^ division of the hydraulic unit cam 182 and varies so .the displacement and the drive ratio of the fluid drive 175 · The regulator 218 is controlled by the output sleeve tooth • ad 146 driven by the gear 224- which on the circumference of the same which is formed with the idle gear 226

m is engaged and this gear wheel in turn drives the gear shown not, which drives with the rotating Sleeve 219 in. connected to controller 218, namely 'For the purpose of! Rotating it at one speed proportional to the speed of the generator rotor 162.

η fig. 8 becomes the control fluid from the charge pump η the sleeve 219 delivered through the passage 216, which is The loading filter 210 extends through the passage 225, which crosses the passage 216 and extends perpendicular thereto. The passage 225 is integral with the end housing 124 A plane is formed which extends radially through the axis of shaft 86.

The loading fluid in passage 225 communicates with an inherently opposite passage 228 via a slotted one Valve 230, which serves to hold a feed pipe 233 back in a division in the shaft 186. The passage 228 3t is also molded in one piece with the housing 124 and unified with a longitudinal it-tube 231 > which protrudes from the end of housing member 124 and extends against the sensor. As can be seen in Figure 18, the pipe is 31 fitted into a valve housing 236 which defines a passage 38 which communicates with the tube 231 for the purpose of delivery on oil fluid communicates to the sleeve 219.

"R controller 213 has" a valve, not shown, which is iial responsive to the speed of controller 218 3d the (JeachwSjäsÄigkeit dee Hülsenstahnr * dee 146 moves

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to selectively deliver fluid through passageway 240 and 241 (FIG. 17) to displacement control 222 and in particular Chamber 243 (Fig. 19) to supply the displacement control.

For the purpose of cooling the stator 161 of the generator 160, charge fluid is supplied in passage 216 to a generally axially extending passage 246 (FIGS. 4 and 6) which is formed in one piece in the housing perimeter 124. As seen in Figures 9 and 11, the passage 246 communicates with the passage 248 which extends generally axially W in the drive housing member 124 to the open end 249 thereof. Passage 248 also appears in dashed lines in Figure 4. The charging fluid in passage 248, which is in fact cooling fluid for the generator stator, passes over the interface of housing members 124 and 122 in passage 2511 which extends axially in generator housing 122 as seen in FIG. The passage 251 communicates through radial passages 253 in the housing member 122 with an arcuate recess 264 (see also FIGS. 2 and 12) which runs almost 360 ° in the housing member 122 adjacent and aligned with the stator 161.

The fluid which flows in the recess 264 is in direct contact with the stator 161 and cools the stator as it flows around the same and exits through the radial passages 266, as can be seen in FIG. 12, similarly in FIG of the construction at radial passages 253. The cooling fluid exits in the opposite seal through an axially extending passage 267 also formed in one piece in housing member 122 and back against interface 242 between the drive and generator housings. As seen in i ⁽¹ fig. 10), the exiting stator cooling fluid from the generator housing 122 enters the drive housing 124 through the

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Passage 268 and horny backwards through the drive housing to a 3-system pressure valve 270, which is shown in FIG. 7. The valve 270 is used to bring fluid to the low pressure side to conduct the hydraulic circuit, not shown, which connects the hydraulic units 177 and 179 to one another, connects.

The excess hydraulic fluid used by the charge pump 200 for the entire hydraulic circuit is supplied via an iadedriiok overflow valve 272 delivered, which in Pig. 7 through passage 274 extending transversely in the drive housing 124 extends, as shown in Fig. 7, to the other oeite of the drive housing, where it is, as in in Pig. 4 is shown opening into a common sump, which discharged and excess fluid for both components into your drive housing 124 and generator housing 122 collects.

jis is understandable from Mg. 3 and 4 that a partition 279 is provided in the drive housing 124, which the drive housing in a reservoir or a tank 280 divided hydraulically by a common sump 282 for both generator and drive housings 122 and 124, respectively is divided. The partition wall 279 extends upwards to the mounting plate 201, which is also a Mounting plate intended for the irrigation pump 285, as described in Pig. is shown. openings, such as at 285 and 286 'in the Mounting plate 201 create a sump connection between the drive housing and the generator housing. It's understandable, that the mounting plate 201, as noted above, is formed with the partition wall 150 between the generator and drive housing. Like in Pig. 3 has the Irrigation pump 283 has an inlet channel 286 which communicates freely with the sump and an outlet channel 288, both of which are formed in the mounting plate 201. The irrigation pump 283

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serves to draw fluid from the common sump in the housings and deliver fluid to the outside of the housings through a suitable purge filter and cooler (not shown in Pig. 2-19) and to return fluid to reservoir 280. As shown in Fig. 14, a generator part 294 of the sump 282 is determined in the generator housing 122, which freely communicates with the interior of the generator housing and the invitation of the flushing pump 283 through channels 285 and 286 *, as shown in Pig, 4 « Jhv Generator sump portion 294 collects excess cooling fluid from the generator as well as lubricating fluid drain from the bearings in the generator housing.

The outlet 288 of the irrigation pump 283 delivers fluid to the passage 290, as seen in FIG. 3, to an irrigation fluid housing outlet 293 shown in FIG.

Appropriate conduits (not shown in Figures 2-19) are provided and connected to conduit 293 to carry the fluid to convey to a cooler, as well as through a flushing filter, such as is shown at 84 and 85 in Fig. 1, and back to an inlet passage 296 formed in the end of the drive housing 124 as shown in FIG. The hydraulic fluid entering channel 296 goes through one Inlet 300 to a conventional vortex chamber 302 * -au of the vortex chamber 302, the filtered and cooled hydraulic fluid flows directly into the reservoir or tank 280 How As seen in Fig. 16, the charge pump 200 has "In Binlaßrohx 304 which, as at 305, opens directly into reservoir 280 so that the hydraulic fluid is cooled and filtered from it sucks.

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The charge pump 200 provides charge fluid for the purpose del * lubrication of the gearbox in the drive, both as for Cooling of the rotor 162 of the generator by direct contact. For this purpose, part of the charging fluid occurs, which flows into passage 225 as in Pig. 8, into the feed tube 233, which is located centrally in the drive housing 124 is mounted, and flows therefrom through an axial passage 308 into the gear carrier 130, as in Pig. 2 is shown. A part This fluid flows radially outward from the carrier to lubricate the adjacent bearings, such as the Bearings 142, 143 and 148.

The charge and cooling fluid flows through passage 308 through diagonal passages 310 in the hollow sleeves 312, / which carry the differential pinions 134 and 135. Part of this Fluid exits between the carrier and the ends of the pinions for the purpose of lubricating the pinions. After slack Fluid flows through sleeves 312 through passages 314 at the other end of the differential pinions and from lort in an axial passage 316, which is also in the carrier is shaped.

Ladial vias 318 are formed in the carrier 130 that are marked with .em iLxialdurchgang 316 in connection, which the ' Outward flow of fluid into rotor sleeve 158 is permitted. > This fluid is moved outwards by centrifugal force thrown and goes through passages 320 in the rotor - ', ole 158 and from there into direct contact with the totor 162. Suitable additional means can be provided yes and no to the cooling flow from the passages or channels > To direct 20 into direct contact with the rotor 162, fluid from the passages 318 can also be used for lubrication of the bearing 322 as shown in Fig. 2 can be used.

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An optional integrated constant speed drive and generator 400 is shown in FIGS. 20-22. This drive and generator combination is similar to that in Pig. 1 and generally similar to that contained in the Fig. 2-19 is disclosed, with the first exception that the differential pinion gears are not partially in the generator rotor sleeve are housed. This reduces the rotor size somewhat and reduces centrifugal forces on the rotor. An additional The difference from Figures 2-19 is that the cooling fluid for the rotor and the lubricating fluid for the differential gear flows from the generator housing to the drive housing, instead of the other way around.

In FIG. 20, the drive and generator 400 can be seen in such a way that it contains a generator housing 401 which has a stationary Generator stator 402 includes, as well as rotatable rotor 403 and exciter connection 404. The right one The end of the rotor shaft 405 is supported in a bearing 406 in the generator housing 401 and the left end of the rotor shaft is carried in a grooved sleeve 410 shown in Fig. 22 which passes through the output of the constant speed drive is driven.

ψ A drive housing 412 is attached to the generator housing 401, which is shown in FIG. 22 reversed with that of FIG. 20. The drive housing 412 carries an input shaft 4H which can be connected to the motor in the bearing 416. The input shaft 414 is connected to drive an elongated gear carrier 418 through a quick disconnect clutch 419. The gear carrier 418 forms part of an elongated differential 421 of similar construction to the embodiment described above.

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In particular, the .Differential 421 contains two Hit zel gears 423 and 424, which are rotatably mounted on sleeves 425 and 426, respectively, are in turn mounted in the elongated gear carrier 418 are. A stepped timing ring gear 428 has internal ones iLin £ jzänne 429 which mesh with the teeth on the gear 424 and an output sleeve ring gear 432 has inner ring gear teeth 433 »which is in driving engagement with pinion 423 stand. As with the other versions, you can appropriately control the speed and direction of the steering gear 428 a constant output speed from the output 432 can be achieved.

The differential is in its right end (as Fig. 22. · shows) supported by bearing 438 which is mounted on a bearing flange 439 attached to the right end of the drive housing 412 is attached. The carrier 418 is in the control gear 428 supported by bearings 440 and 441,

uac; limce end of differential 421 is in bearings 442 and 443 which are mounted centrally in the left end of the housing 412, as shown in Pig * 22, which is the output sleeve gear 432 carries. The left end of the differential gear carrier 418 is in the output ring gear 432 through dae Bearing 445 supported. The internally grooved generator coupling sleeve 410 is through with output sleeve gear 432, an overrunning clutch 446 additionally connected to a bearing 447.

It is understandable that the input shaft 414 and the Differential 421 are supported with the drive housing. Also in the drive housing are two hydraulic ones .drives 450 worn (only one in the two apartments shown iat), similar in construction to the hydraulic Drive 175, which is in Pig. 2 is shown. The precaution of

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two hydraulic actuators 450 reduces the required diameter of the drive housing 412. £ s is sufficient to determine an end of each of the drives as in the ⁿ i DAT ig. 22 is connected to gear carrier 418 by gear 451 and gear 452, while the other end of each of the drives is connected to control gear 428 by gear 454 and gear 455. By changing the direction and amount of displacement of cam 459, the speed and sealing of the timing gear 428 can be changed and a constant output speed can be obtained from the output gear 432.

It will be understood that input shaft 414 and differential 421 are coaxial with respect to housing 412 both such as the casing 401 for the generator are arranged in a similar manner to the embodiments previously described even though they are in Pig. 22 appear offset because this is an irregular sectional view.

For the purpose of maintaining a constant output speed, a control regulator 457 (including 21) is provided which is driven by output ring gear 432 through gear 459 '. The controller 457 selectively directs fluid to a control motor which varies the displacement of the squat 459 to achieve a constant speed of the generator rotor 403.

The gear wheel 459%, which is driven by the output, also drives the gear wheel 461, which comes from an Itüok the shaft 462 is formed, which in turn drives both a wash pump 463 and a charge pump 464, both of which are coaxially mounted in the drive housing 412 »

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In addition to the flushing pump 463, there is a generator flushing pump «■ 67 provided in the drive housing 412 for the purpose of read generator housing 401 to flush.

) The drive housing 412 has a separate reservoir 470 (Pig. md 21), which communicates with the inlet of the charge pump 264, im to deliver filtered and cooled fluid to it.

-) The charge pump 464 delivers fluid through a reverse with the axially extending passage 464 'in the housing 412 i a charge fluid filter 468 (Figures 21 and 22).

Fluid flows from the charge filter through passage -72 (Fig. 21) to hydraulic actuators 450 through passage r80 for the purpose of bringing fluid to the working lines of the .supply hydraulic drive 450. Further becomes charge fluid supplied through line 482 to Hegler 457 except that charge fluid is returned to it is supplied in a sump 483 in the drive housing.

for the purpose of cooling the generator and for lubrication '.es Jifferentiales fluid flows out of the line .through conduit 486 to nozzles 487 and 488 which cool fluids in direct contact with the stator 402.

Fluid in passage 486 also goes down to the 2nde of the generator housing and into a central passage f90 (Fig. 20), which is centrally located in the generator rotor shaft 405 is in order. The radial passages 492 and 493 in the ienera.torrotor 405 are used to supply cooling fluid to the iotor 403 of the generator for direct contact cooling of the same to squirt.

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The remaining fluid in passage 490 goes through the end of the rotor shaft 405 and into a fitting tube 496, which 22 and which is inserted into the gear carriers 418. This Hohr has "limited outlet to the Grooves and the coupling 419 to lubricate and the rest goes through the central passage therein, through diagonal channels 498 the interior of pinion sleeves 425 and 426. Part of the fluid inside goes out to lubricate the pinion gears and the remainder part goes through passages 501 in the gear carrier 418 on the other side of the pinion. Some of this fluid goes along grooves 503 and 504 for the purpose of lubrication thereof and the remainder goes out through radial passages 506 in the input connection from shaft 414 into drive sump 483.

The generator wash pump 467 transports fluid through line 508 to the reservoir 470 in the housing 412 (shown in Pig. 21). The drive flush pump 463 conveys fluid through the passage 510 from the drive housing through a Cooler 512. Cooling fluid is supplied from cooler 512 to the Drive housing 412 and returned to tank 470 through the swirl chamber.

ψ A suitable lower speed switch 514 as shown in FIG. 21 is shown to be provided, which is connected to the controller 457, for the purpose of separation of the Gfeneratorausganges from the other generators on the aircraft at a predetermined abnormal underspeed. An injector 515 is provided to pressurize the propulsion and generator housing and a charge spill valve 516 returns excess charge fluid directly to the reservoir or tank 470, if desired a boost switch 517 may be provided to remotely display the boost level.

- 25 -

109814/1635

Claims (2)

- 25 patent claims 1. Drive and generator combination with a generator that comprises a stationary stator and a rotor driven at a substantially constant speed a constant speed drive to drive the rotor including an input shaft member, which can be driven by a prime mover, an output shaft member which is used to drive of the rotor is connected to a differential gear between the input and output shaft members including one Control gear to change the speed of the output shaft member with respect to the input shaft member, a first hydraulic unit that is drivingly connected to a of the shaft members is connected, a second hydraulic unit which is drivingly connected to the control gear is a conduit means hydraulically connecting the first and second hydraulic units to one another, and control means for changing the displacement of one of the hydraulic units by substantially one maintaining constant rotor speed, characterized in that said differential a gear carrier in lines with the input shaft member and with the output member, the control gear in line with the input shaft member and the Output shaft element let, and where the output shaft element is directly connected to the said rotor, whereby the need for a drive gear between the different! al s output member and the rotor is avoided. 2. Combination according to claim 1, characterized by duroh tine third hydraulic unit, the opposite with dt » - 26 - 109814 / 163S a shaft link connected let, a fourth hydraulic Unit that is drivingly connected to the control gear is a second conduit means which the third and connecting fourth hydraulic units to one another, a second control device for changing the displacement of at least one of the third and fourth hydraulic units in back-to-back relationship and with With respect to the axis of the input and output shaft members are offset, the third and fourth hydraulic units in back-to-back relationship and with respect to the input and output shaft members are offset. 1098U / 1635 Blank page